Cooling module with parallel blowers

ABSTRACT

A cooling system for an electronics chassis includes a plurality of centrifugal blowers arranged to motivate cooling air through the electronics chassis. The centrifugal blowers are arranged in one or more sets, each having blowers oriented with respective inlets in mutual facing relationship. The orientation, positioning, and alignment of the centrifugal blowers facilitates a compact arrangement of the plurality of blowers that achieves increased aerodynamic efficiencies to reduce noise output and energy consumption.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation in part of U.S. patent application Ser. No. 13/534,722, filed on Jun. 27, 2012 and entitled “Cooling Module with Parallel Blowers”, which claims priority to U.S. provisional Patent Application Ser. No. 61/501,535, filed on Jun. 27, 2011 and entitled “Cooling Module with Parallel Blowers”, the contents of which being incorporated herein in their entirety.

FIELD OF THE INVENTION

The present invention relates to cooling systems generally, and more particularly to cooling fan arrays specifically arranged for enhanced performance in motivating cooling fluid through an electronics chassis.

BACKGROUND OF THE INVENTION

Designers of electronic equipment have become increasingly challenged to provide high-power devices in relatively small packages. These devices require compact and highly efficient cooling systems. A typical cooling system involves moving air across one or more printed circuit boards. The flow path layout, type of air moving device, and how well it is integrated into the system are all key elements in achieving the desired performance in a small package size with limited noise.

One such electronic device is a telecommunications router which typically includes a series of electronics communications “cards” arrayed with cooling fans in a chassis. The desire to make routers more powerful, yet compact in size, leaves little space for cooling system components necessary to address ever-increasing heat loads. Conventional system designs often employ fans that are not well matched to the system pressures, or do not move air efficiently within the space constraints, and result in unacceptable noise and relatively large power consumption.

Design efforts to date typically use multiple axial fans arranged in a “tray”, as illustrated in FIG. 1. The fans either push cooling air through a chassis or pull warm air out from the chassis. Higher fan speeds have been used to address increased flow requirements, but as system pressures increase, designers have responded by adding additional trays of axial fans arranged in series. An example of such series of axial fan trays is illustrated in FIG. 2. In theory, each axial fan tray handles half of the system pressure. The conventional arrangement illustrated in FIG. 2 sets forth an orientation with both fan trays downstream from the electronics being cooled in the electronics chassis, thereby pulling cooling air through the system. In other conventional arrangements, fan trays may be disposed upstream of the electronics being cooled, or fan trays being disposed both upstream and downstream of the electronics in a push-and-pull-through system. Relatively high aerodynamic efficiencies may be achieved with this type of air mover, but unfortunately require high rotational speeds that typically result in unacceptable acoustic levels, and assume relatively large module volumes that may not integrate well in space-constrained chassis designs.

Centrifugal blowers are better suited for the higher pressures encountered in high cooling load applications. However, centrifugal blowers have not typically been considered for electronics chassis cooling, particularly in compact arrangements, due to their relatively larger physical size. As a result, centrifugal blowers have not commonly been considered for fit within cooling system packaging space. For example, a single inlet centrifugal blower sized to match the performance of two axial fans in series can require twice the volumetric space, be less efficient, and result in a less uniform flow field.

It is therefore an object of the present invention to provide a cooling system that simultaneously increases performance and reduces noise of conventional air movers.

It is a further object of the present invention to provide a cooling arrangement that is particularly well suited for cooling densely populated electronic components, such as telecommunication edge routers.

SUMMARY OF THE INVENTION

By means of the present invention, enhanced cooling to electronics chassis may be achieved with greater efficiency and reduced acoustic levels. The present cooling system provides cooling fluid, such as cooling air, in a generally uniform flow field across electronic components for cooling thereof. The electronic components may be disposed in a chassis, such as a telecommunication edge router, server, or a power supply unit.

In one embodiment, a cooling fan array of the present invention is arranged for motivating cooling fluid through an interior chamber of an electronics chassis generally along a flow direction. The cooling fan array includes a frame having a cooling fluid entrance and a cooling fluid exit in fluid communication with the interior chamber, with at least one of the frame entrance and exit directing air flow therethrough along a direction parallel with the flow direction. The frame further includes a plurality of modules each including a centrifugal blower with an impeller driven by a motor and defining an axis of rotation, wherein the blower includes an inlet arranged to intake the cooling fluid along a respective intake direction transverse to the flow direction. The blowers are arranged in the frame in one or more sets, with each set including at least two blowers oriented with respective inlets in facing relationship with one another and with respective axes of rotation being axially aligned with one another, the facing inlets being axially spaced apart by a spacing dimension that is less than 75% of a diameter dimension of the impeller within the set, such that the blowers operate in parallel to motivate the cooling fluid through the cooling fluid entrance. The modules define a height dimension between the cooling fluid entrance and the cooling fluid exit of 40-50 mm.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an illustration of an axial fan tray arrangement of the prior art;

FIG. 2 is a schematic diagram of an axial-type fan tray arrangement in series of the prior art;

FIG. 3 is an illustration of a cooling fan array of the present invention;

FIG. 4 a is a schematic illustration of an electronics chassis of the present invention incorporating the cooling fan array of FIG. 3;

FIG. 4 b is a schematic illustration of an electronics chassis of the present invention incorporating a cooling fan array of the present invention;

FIG. 5 a is a schematic illustration of an electronics chassis of the present invention incorporating a cooling fan array of the present invention;

FIG. 5 b is a schematic illustration of a cooling fan array of the present invention;

FIG. 5 c is a schematic illustration of a cooling fan array of the present invention;

FIG. 6 is a chart depicting performance characteristics of a cooling fan array of the present invention;

FIG. 7 a is a schematic illustration of an electronics chassis of the present invention incorporating a cooling fan array of the present invention;

FIG. 7 b is a schematic illustration of a portion of the cooling fan array illustrated in FIG. 7 a;

FIG. 8 a is a schematic illustration of a portion of a cooling fan array of the present invention; and

FIG. 8 b is a schematic illustration of the portion of the cooling fan array illustrated in FIG. 8 a.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

The objects and advantages enumerated above together with other objects, features, and advances represented by the present invention will now be presented in terms of detailed embodiments described with reference to the attached drawing figures which are intended to be representative of various embodiments of the invention. Other embodiments and aspects of the invention are recognized as being within the grasp of those having ordinary skill in the art.

With reference now to the drawings, and first to FIGS. 3 and 4 a, a cooling fan array 10 includes a frame 12 having a cooling fluid entrance 14 and a cooling fluid exit 16. Frame 12 includes a plurality of modules 18 a-18 c that are individually removable from and replaceable in frame 12 without operational interruption to others of modules 18 a-18 c. Such a characteristic is known in the art as being “hot swappable”, in that each of modules 18 a-18 c may be removed from frame 12 for repair or replacement without interrupting or substantially affecting the operation of the remaining modules 18 a-18 c of housing 12. In this manner, maintenance may be performed upon a respective module 18 a-18 c without requiring shut down of the entire cooling fan array 10, which would require shut down of the electronics chassis being cooled by cooling fan array 10. In some cases, removal of one or more of modules 18 a-18 c from housing 12 requires increased blower speed in the remaining modules to accommodate and maintain a desired cooling fluid flow rate through the electronics chassis. Control systems for electronically controlling the blowers of hot-swappable modules for air-cooling systems are well understood in the art.

Each of the modules 18 a-18 c in frame 12 may include one or more double-width double-inlet forward curved (DWDI-FC) centrifugal blowers 20. In the example arrangement of FIG. 3, frame 12 includes three modules 18 a-18 c, each of which includes three DWDI-FC centrifugal blowers 20. It is to be understood, however, that frame 12 of the present invention may include any number of a plurality of modules 18 a-18 c, with each module having, for example, one or more DWDI-FC centrifugal blowers 20. Moreover, modules 18 a-18 c of frame 12 may include different numbers of DWDI-FC blowers 20. In typical embodiments, each DWDI-FC centrifugal blower 20 a-20 c is driven by a motor, such as a DC brushless motor that is independently controllable by a control system to adjust and maintain desired cooling air flow characteristics through frame 12 and the associate electronics chassis.

FIG. 4 a illustrates frame 12 secured to an electronics chassis 30 in an embodiment wherein cooling fan array 10 is arranged to pull air flow through a series of electronics communication cards arrayed in an interior chamber 32 of electronics chassis 30 generally along a flow direction 34 to cool the electronic components disposed at interior chamber 32 of electronics chassis 30. Cooling fluid flow (represented by arrows) is drawn through electronics chassis 30 from an inlet 36, into cooling fluid entrance 14 of frame 12, and finally out from cooling fan array 10 at cooling fluid exit 16. Centrifugal blowers 20 in parallel motivate the cooling fluid flow along flow direction 34, and motivate the cooling fluid flow “in parallel” by each blower individually acting upon cooling fluid flow through interior chamber 32 of electronics chassis 30. In addition, blowers 20 a-20 c of each of modules 18 a-18 c motivate the cooling fluid flow “in parallel” by receiving cooling fluids to their respective inlets that is sourced directly from cooling fluid passing through interior chamber 32, and not as exhaust from an “upstream” blower within its associated frame 12. It is contemplated that a plurality of frames 12 may be employed in a cooling fan array 10, wherein the respective frames 12 may operate in series to motivate cooling fluid through electronics chassis 30. In such case, blowers 20 of a “downstream” housing 12 would in fact receive the exhaust from an “upstream” blower. However, the blowers 20 within a respective frame 12 operate in parallel to receive substantially only “fresh” air entering frame 12 through cooling fluid entrance 14.

Blowers 20, such as blowers 20 aa-20 ac each include dual opposed inlets 22, 24 arranged to intake the cooling fluid along respective intake directions 26, 28 which are transverse to flow direction 34. Such an arrangement is best viewed in FIG. 4 b, which is identical to the system illustrated in FIG. 4 a with the exception of the cooling fluid outlet directionality. Cooling fluid exit 16 of the embodiment illustrated in FIG. 4 a is transverse to flow direction 34, while cooling fluid exit 16 of the embodiment illustrated in FIG. 4 b permits outflow parallel to flow direction 34. It is contemplated that frame 12 may be provided, in some embodiments, with any suitable cooling fluid outlet arrangement and orientation, including for either or both of cooling fluid outlet directions transverse or parallel to flow direction 34.

In some embodiments, each of blowers 20 include a single-scroll blower housing 42 which defines the dual-opposed inlets 22, 24 and a blower outlet 44. Centrifugal blowers 20 may further include a forward-curved impeller having a diameter dimension “y”, and defining an axis of rotation 52 which extends through inlets 22, 24 substantially transverse to flow direction 34. Blowers 20 each include a motor 54 for rotation of the respective impellers about their rotation axis 52. In the illustrated embodiments, respective blowers 20 in modules 18 define sets 41 of axially adjacent blowers. For example, blowers 20 aa-20 ac, as shown in FIG. 4 b, represent a set 41 a of blowers having respective impellers that axially aligned about axis of rotation 52. In this example, blower 20 aa is a part of module 18 a, blower 20 ab is a part of module 18 b, and blower 20 ac is a part of module 18 c. Thus, set 41 a of blowers 20 aa-20 ac may include one or more blowers from a plurality of distinct modules 18 a-18 c. In other embodiments, however, blower sets 41 a-41 c may be confined to a plurality of blowers within a single respective module 18 a-18 c. Blower sets 41 a-41 c preferably include a plurality of centrifugal blowers 20 that are arranged in frame 12 with their respective impeller axes of rotation axially aligned with one another, with axially adjacent inlets of axially adjacent blowers 20 being in mutually facing relationship. In the illustrated embodiment, blowers 20 a-20 c of blower set 41 a are DWDI-FC centrifugal blowers having respective impeller axes of rotation aligned along axis 52. Axially adjacent blower inlets 24 a, 22 b and 24 b, 22 c are in facing relationship with one another drawing inlet air in opposite directions and transverse to flow direction 34, as depicted by the air flow arrows in FIG. 4 b. This arrangement has been discovered by the applicant to improve air flow efficiencies in motivating air flow through electronics chassis 30.

In some embodiments, adjacent blower inlets 24 a, 22 b and 24 b, 22 c are not only axially aligned, but also spaced apart by a specific spacing dimension “x”. In some embodiments, such spacing dimension “x” may be less than about 0.75 (75%) of diameter dimension “y” of the impeller of blowers 20, and more preferably between 0.5 and 0.75 (50%-75%) of diameter dimension “y” of the impeller of blowers 20. In the event that the diameter dimension “y” of the axially adjacent pair of blowers is not equal, the spacing dimension “x” may be determined as 0.5-0.75 (50-75%) of the diameter dimension “y” of the larger impeller. Similarly, a spacing dimension “z” between a blower inlet and an axially adjacent wall, such as between blower inlet 22 a and a side wall 9 of frame 12, may be between about 0.2-0.5 (20-50%) of diameter dimension “y” of the respective blower impeller, and more preferably between 0.23-0.36 (23-36%) of the respective impeller diameter dimension “y”.

The arrangements illustrated in FIGS. 4 a and 4 b have been found to provide surprisingly enhanced aerodynamic efficiency for each blower 20, such that total power input to motivate a desired cooling fluid flow may be reduced. In addition, the surprising efficiency of the proposed arrangement reduces sound emissions, which is also a beneficial operating characteristic of the cooling fan arrays of the present invention. Such enhancements in efficiency and sound reductions may be accomplished in a housing volume that is not substantially larger than the volume assumed by conventional fan trays. Therefore, it is believed that the arrangements of the present invention substantially improve cooling fan arrays.

Applicants are particularly surprised to discover that the small axial spacing between adjacent blower inlets, and between a blower inlet and an axially adjacent wall, does not diminish aerodynamic performance in the operation of the centrifugal blowers. FIG. 6 is a graphical depiction of aerodynamic performance curves at various relative dimensions for spacing “A”, wherein spacing “A” may be between a blower inlet and an axially adjacent wall, equivalent to spacing dimension “z” in FIG. 4 b, or one-half of the spacing dimension between axially adjacent inlets, equivalent to spacing dimension “x”/2. As depicted in FIG. 6, the present arrangement of axially aligned centrifugal blowers with a spacing “A” of 36% of the impeller diameter exhibits aerodynamic performance that is equivalent to centrifugal blowers with “unrestricted” inlets, which are defined as having a spacing “A” that is sufficiently large to avoid disturbance to inlet air flow. In effect, therefore, the “unrestricted inlet” data in FIG. 6 assumes an infinite spacing “A”.

The data graphically depicted in FIG. 6 reveals a surprising result of the present invention, in that a centrifugal blower arrangement with a spacing “A” of 36% of an impeller diameter dimension “y” of the blower applied to motivating air through an interior chamber 32 of electronics chassis 30, as depicted by the “system curve” of FIG. 6, exhibits substantially equivalent aerodynamic performance to centrifugal blowers with unrestricted inlets. Such a discovery is counter to conventional understanding of centrifugal blower aerodynamic performance, wherein restricted inlet spacing “A” consistently reduces aerodynamic performance of the blower. Applicants have surprisingly discovered that, even with centrifugal blower inlets “restricted” with a spacing “A” of 36% of the impeller diameter, can achieve aerodynamic performance equivalent to centrifugal blowers with unrestricted inlets, as measured in a cooling system application. FIG. 6 further reveals that the present arrangement of axially aligned centrifugal blowers with a spacing “A” of 23% of the impeller diameter, as applied in motivating air through chassis 30, is substantially equivalent to conventional centrifugal blower arrangements with a spacing “A” of 50% of the impeller diameter.

Applicants theorize that the discovery of unexpected aerodynamic performance at small spacing dimensions between adjacent centrifugal blowers may be at least in part the result of coinciding vortices just upstream from the respective blower inlets, wherein the coincidence of the vortices is created as a consequence of the small axial spacing dimensions. The coincident vortices may be synergistic in generating a highly efficient aerodynamic flow into the respective blower inlets. Such a finding is contrary to conventional understanding, which predicts aerodynamic performance degradation with the presence of another operating blower within the flow field of the first blower. The results depicted in FIG. 6 clearly indicate otherwise.

The arrangement illustrated in FIG. 4 b includes a frame 12 incorporating a separation plate 62 defining an outlet plenum 64 of frame 12 which primarily separates inlets 22, 24 of blowers 20 from respective outlets 44. Outlet plenum 64 is therefore fluidly connected to cooling fluid entrance 14 only through blowers 20, such that cooling fluid is motivated through interior chamber 32 of electronics chassis 30 into cooling fluid entrance 14 and into respective inlets 22, 24 of blowers 20 for exhaust out through blower outlets 44, and ultimately out through cooling fluid exit 16. Thus, outlet plenum 64 is fluidly connected to cooling fluid exit 16.

Separation plate 62 creates separation between a negative pressure side 13 from a positive pressure side 11 of frame 12. Separation plate 62 therefore eliminates the need for separate ducts from each blower 20 in a module 18, and reduces recirculation to negative pressure side 13 in the event of blower failure. The need for back draft dampers is therefore substantially reduced or eliminated. As illustrated in FIG. 3, each module 18 a-18 c may include a separation plate 62 a-62 c for separating positive and negative pressure sides 11, 13 of a respective module 18. Outlet plenum 64 may further be divided by divider plates 63 a, 63 b to define individual module outlet plenums 64 a-64 c. Divider plates 63 a, 63 b segment outlet plenum 64 as individual outlet zones from the blowers of each module 18 a-18 c.

Outlets 44 of blowers 20 may be canted at an angle, such as at 45°, to promote cooling fluid exhaust more directly out through cooling fluid exit 16 along an outlet axis 58 that is substantially transverse to flow direction 34. In other embodiments, such as that illustrated in FIG. 4 b, blower outlets 44 may be directed axially in parallel with flow direction 34 to direct exhaust cooling fluid axially out from cooling fluid exit 16.

The systems illustrated in FIGS. 4 a and 4 b depict a “pull” system employing a plurality of DWDI-FC centrifugal blowers arranged to motivate the cooling fluid flow in parallel, and with parallel cooling fluid discharges. Moreover, the respective inlets 22, 24 of blowers 20 are arranged transverse to flow direction 34. Such arrangement represents a substantial noise reduction in comparison to similar packaging space allocated for conventional axial fan trays.

A further embodiment is illustrated in FIG. 5 a, wherein cooling fan array 110 includes a frame 112 having a cooling fluid entrance 114 and a cooling fluid exit 116. Frame 112 includes a plurality of modules 118 a-118 c that are individually removable from and replaceable in frame 112 without operational interruption to others of modules 118 a-118 c. In this embodiment, each of the modules 118 in cooling fan array 110 includes one or more sets of “forward-curved” centrifugal blowers 180. In the example arrangement of FIG. 5 a, each set of forward curved centrifugal blowers 180 includes two centrifugal blowers 182 a, 182 b placed back to back, such that inlet 184 a of blower 182 a is oppositely disposed from inlet 184 b of blower 182 b. Due to such opposite orientations, the respective impellers of blowers 182 a, 182 b may be configured to rotate in opposite circumaxial directions with respect to one another about an axis of rotation 152. The opposite circumaxial rotational directions have been found to generate desired cooling fluid flow characteristics through frame 112 and interior chamber 132. Blower sets 180 may include two or more blowers 182 a, 182 b which may be arranged to coordinate with other blowers of the module 118 and/or array 110 to motivate cooling fluid flow through interior chamber 132 of electronics chassis 130. Blower sets 180 may operate to motivate the cooling fluid flow along flow direction 134, and to motivate the cooling fluid flow “in parallel”.

In the illustrated embodiment, each module 118 a-118 c includes two sets 180 of forward-curved centrifugal blowers 182 a, 182 b. Frame 112 of the present invention, however, may include any number of a plurality of modules 118 a-118 c, with each module having one or more sets 180 of blowers 182. In some embodiments, respective sets 180 of blowers 182 a, 182 b among a plurality of modules 118 may be arranged so that their respective axes of rotation through inlets 184 a, 184 b are all substantially mutually aligned along a respective axis 152, 154. In typical embodiments, each blower 182 may be driven by a motor, such as a DC brushless motor that is independently controllable by a control system to adjust and maintain desired cooling fluid flow characteristics through frame 112 and the associated electronics chassis 132.

Blowers 182 each include a respective inlet 184 that is arranged to intake the cooling fluid along a respective intake direction 126, 128 which is transverse to flow direction 134. In the embodiment illustrated in FIG. 5 a, cooling fluid exit 116 permits outlet flow from blowers 182 along an outlet direction 135 that is substantially transverse to flow direction 134. It is contemplated, however, that frame 112 may be provided with any suitable cooling fluid exit arrangement and orientation, including for either or both of cooling fluid outlet directions transverse or parallel to flow direction 134.

It is contemplated that the blower sets 180 may be configured to provide desired cooling fluid flow in a manner similar to blowers 20 described hereinabove. Blower sets 180, however, utilize, for example, single-inlet forward-curved centrifugal blowers placed in back to back relationship to together motivate cooling fluid flow through electronics chassis 130. In some embodiments, respective blowers 182 a, 182 b may be in abutting relationship with one another, or may be spaced apart by a desired spacing dimension. Moreover, mutually facing inlets of axially adjacent blowers may preferably have a spacing dimension “x₁” of less than about 0.75 (75%) of a diameter dimension “y₁” of the impellers of respective blowers 182 a, 182 b, and more preferably between 0.5-0.75 (50-75%) of diameter dimension “y₁”. The respective inlets 184 a, 184 b of blowers 182 a 182 b lead to impellers which may preferably be axially aligned along a respective axis of rotation.

Another embodiment is illustrated in FIG. 5 b wherein cooling fan array 210 includes a frame 212 having a cooling fluid entrance 214 and a cooling fluid exit 216. Frame 212 includes a plurality of modules 218 a-218 c that are individually removable from and replaceable in frame 212 without operational interruption to others of modules 218 a-218 c. In this embodiment, each of the modules 218 in cooling fan array 210 includes one or more sets of centrifugal blowers 280, which may include forward-curved impellers. In the illustrated embodiment, each set of centrifugal blowers 280 includes two centrifugal blowers 282 a, 282 b placed in facing relationship to one another, such that inlet 284 a of blower 282 a is in generally facing relationship with inlet 284 b of blower 282 b. The respective impellers of blowers 282 a, 282 b may be configured to rotate in opposite circumaxial directions with respect to one another about an axis of rotation 252. Blower sets 280 may be arranged to coordinate with other blowers of the respective module 218 and/or array 210 to motivate cooling fluid flow through the associated electronics chassis 230. Blower sets 280 may operate to motivate the cooling fluid flow along flow direction 234, and to motivate the cooling fluid flow “in parallel”.

In the illustrated embodiment, each module 218 includes one set 280 of centrifugal blowers 282 a, 282 b. Frame 212 of the present invention, however, may include any number of a plurality of modules 218, with each module 218 having one or more sets 280 of blowers 282. In typical embodiments, each blower 282 may be driven by a motor, such as a DC brushless motor that is independently controllable by a control system to adjust and maintain desired cooling fluid flow characteristics through frame 212 and the associated electronics chassis 232.

Blowers 282 each include a respective inlet 284 that is arranged to intake the cooling fluid along a respective intake direction 226, 228 that is transverse to flow direction 234. In the embodiment illustrated in FIG. 5 b, cooling fluid exit 216 permits outlet flow from blowers 282 along an outlet direction 235 that is in alignment/parallel to flow direction 234. It is contemplated, however, that frame 212 may be provided with any suitable cooling fluid outlet arrangement and orientation, including for either or both of cooling fluid outlet directions transverse or parallel to flow direction 234.

It is contemplated that the blower sets 280 may be configured to provide desired cooling fluid flow in a manner similar to blowers 20, 182 described above. Blower sets 280, however, utilize, for example, single-inlet forward-curved centrifugal blowers placed in substantially face to face relationship to together motivate cooling fluid flow through electronics chassis 230. Respective blowers 282 a, 282 b may be spaced apart by a desired spacing dimension “x₂” that is less than about 0.75 (75%) of the diameter dimension “y₂” of the impellers of blowers 282 a, 282 b, and more preferably between 0.5-0.75 (50-75%) of diameter dimension “y₂”. The respective inlets 284 a, 284 b of blowers 282 a, 282 b lead to impellers which are preferably axially aligned along a respective axis of rotation 252, 254.

A still further embodiment is illustrated in FIG. 5 c wherein cooling fan array 310 includes a frame 312 having a cooling fluid entrance 314 and a cooling fluid exit 316. Frame 312 includes a plurality of modules 318 a-318 c that are individually removable from and replaceable in frame 312 without operational interruption to others of modules 318 a-318 c. In this embodiment, each of the modules 318 in cooling fan array 310 includes one or more sets of centrifugal blowers 380. In the example arrangement of FIG. 5 c, each set of centrifugal blowers 380 includes two centrifugal blowers 382 a, 382 b placed front to front in generally facing relationship with one another, such that inlet 384 a of blower 382 a is in facing relationship with inlet 384 b of blower 382 b. The respective impellers of blowers 382 a, 382 b may be configured to rotate in opposite circumaxial directions with respect to one another about an axis of rotation 352. Blower sets 380 may include two or more blowers 382 a, 382 b which may be arranged to coordinate with other blowers of the module 318 and/or array 310 to motivate cooling fluid flow through the interior chamber of electronics chassis 330. Blower sets 380 may operate to motivate the cooling fluid flow along flow direction 334, and to motivate the cooling fluid flow “in parallel.”

In the illustrated embodiment, each module 318 includes one set 380 of forward-curved centrifugal blowers 382 a, 382 b. Frame 312 of the present invention, however, may include any number of a plurality of modules 318, with each module having one or more sets 380 of blowers 382. In some embodiments, respective sets 380 of blowers 382 a, 382 b among a plurality of modules 318 may be arranged so that their respective inlets 384 a, 384 b are all substantially mutually aligned along a respective axis of rotation 352. In typical embodiments, each blower 382 may be driven by a motor, such as a DC brushless motor that is independently controllable by a control system to adjust and maintain desired cooling flow characteristics through frame 312 and the associated electronics chassis 332.

Blowers 382 each include a respective inlet 384 that is arranged to intake the cooling fluid along a respective intake direction 326, 328 which is transverse to flow direction 334. In the embodiment illustrated in FIG. 5 c, cooling fluid outlet 316 permits outlet flow from blowers 382 along an outlet direction 335 that is substantially transverse to flow direction 334.

It is contemplated that the blower sets 380 may be configured to provide desired cooling fluid flow in a manner similar to blowers 20, 182, 282 described hereinabove. Blower sets 380, however, utilize, for example, single inlet forward curved centrifugal blowers placed in substantially face to face relationship to together motivate cooling fluid flow through electronics chassis 330. In some embodiments, respective blowers 382 a, 382 b may preferably be spaced apart by a desired spacing dimension “x₃” that is less than about 0.75 (75%) of a diameter dimension “y₃” of the impellers of blowers 282 a, 282 b, and more preferably between 0.5-0.75 (50-75%) of diameter dimension “y₃”. The respective inlets 384 a, 384 b of blowers 382 a, 382 b lead to impellers which are preferably axially aligned along a respective axis of rotation 352.

Another embodiment of the invention is illustrated in FIG. 7 a, wherein frame 412 is secured to electronics chassis 430 so that cooling fan array 410 is arranged to pull air flow through a series of electronics communication cards arrayed in an interior chamber 432 of chassis 430. Frame 412 includes a plurality of modules 418 a-418 c that are individually removable from and replaceable in frame 412 without operational interruption to others of modules 418 a-418 c. Blowers 420 (420 a-420 x) typically include a single-scroll blower housing which defines dual-opposed inlets and a blower outlet 444. Such blower outlet 444 may be bifurcated into individual outlet portions 444 a, 444 b, corresponding to respective inlets of blower 420.

In this embodiment, modules 428 a-428 c include individual separation plates 462 a-462 c that, in combination, define an outlet plenum 464, and to aerodynamically separate inlets 422, 424 of blowers 420 from outlet plenum 464. Outlet plenum 464 is therefore fluidly connected to chamber 432 only through blowers 420, such that cooling fluid is motivated through interior chamber 432 of electronics chassis 430 into respective inlets 422, 424 of blowers 420 for exhaust out through blower outlets 444, and ultimately out through cooling fluid exit 416. Thus, outlet plenum 464 is fluidly connected to cooling fluid exit 416.

The individual separation plates 462 a-462 x in combination create a separation between a negative pressure side 413 and a positive pressure side 411 of frame 412. Preferably, individual separation plates 462 a-462 x substantially abut one another or are secured to respective attachment mechanisms in frame 412 to create a substantially continuous separation structure to define the outlet plenum 464 at positive pressure side 411 of frame 412 that is aerodynamically separated from negative pressure side 413. Openings in separation plates 462 may preferably be sized to receive outlets 444 of blowers 420 in a manner that minimizes or prevents leakage from positive pressure side 411 to negative pressure side 413, including in the event of a blower failure.

A height dimension “h” may be defined as the height of frame 412, commonly referred to as the “deck height” of the array of blowers 420 in respective modules 418. One aspect of the present invention is the substantial reduction in the height dimension “h” achievable through the presently proposed centrifugal blower array, in comparison to the height dimension required of conventional cooling fan arrays, while nevertheless achieving system flow and pressure requirements. In some embodiments, height dimension “h” may be between 40-50 mm. It has been discovered by the Applicants that the presently proposed array configurations of centrifugal blowers may exhibit similar flow and pressure to conventional cooling fan arrays that are more than double the presently proposed height dimension “h”. Systems employing the proposed centrifugal blower arrays may therefore opt to reduce overall size requirements, increase flow and pressure requirements, reduce power consumption and noise output, or combinations thereof.

One result of the space savings described above and facilitated by the presently proposed array configuration of centrifugal blowers is the capability of designing outlet plenum 416 in a manner that enhances the operating efficiencies of the centrifugal blowers, typically within a space that would otherwise be occupied by conventional cooling fan tray sets. An example arrangement for outlet plenum 464 is illustrated in the cross-sectional view of FIG. 8 a, wherein outlet plenum 464 may include divergent outlet ducts 472 for conveying cooling fluid exhaust from blower outlets 444 to cooling fluid exit 416. In this embodiment, individual exhaust ducts 472 may be associated with one or more respective blower outlets 444. In the illustrated embodiment, each exhaust duct 472 is associated with a respective pair of cooling outlet openings 444 a, 444 b of an outlet 444 of a respective double inlet centrifugal blower 420. Other arrangements for exhaust ducts 472, however, are also contemplated by the present invention.

Each exhaust duct 472 may be divergent, by forming a larger outlet cross-sectional area “A_(o)” distal from blower outlet 444 than the corresponding cross-sectional area of the inlet “A_(i)” of the respective outlet duct 472 proximal to blower outlet 444. The increasing cross-sectional area of outlet duct 472, in the illustrated embodiment, is formed by the divergently arranged front and rear walls 474, 476 of each outlet duct 472. Side walls 478, 480 are, in the illustrated embodiment, substantially parallel, while front and rear walls 474, 476 are angularly skewed to diverge from one another, as taken from a position proximal to blower outlet 444 to a position of outlet duct 472 distal to blower outlet 444. Inlet cross-sectional area A_(i) may be defined by the smaller one of the area defined by the perimeter wall of blower outlet 444, and the opening of outlet duct 472 at or proximal to blower outlet 444. The outlet cross-sectional area A_(o) of outlet duct 472 may be defined by the area of the opening of outlet duct 472 at upper plate 480, which may also define the boundary to cooling air exit 416.

The extent of divergence from the inlet portion to the outlet portion of outlet duct 472 may be dependent upon a number of factors, including space constraints, air velocity, air directionality, and so on. It is to be understood, however, that the divergent outlet ducts 472 are intended to be suitable to recover velocity pressure by converting a portion of the velocity pressure energy to a static pressure. For example, a 50% reduction in velocity pressure between blower outlet 444 and outlet 473 of outlet duct 472 improves a 40% total efficiency blower to nearly 55% total efficiency. The conversion of velocity pressure to static pressure at outlet ducts 472 improves the efficiency of blowers 420, thereby permitting blowers 420 to be operated at lower speeds, which leads to reduced power consumption, reduced noise output, and increased life span.

It is to be understood that a variety of configurations of outlet ducts 472 are contemplated by the present invention, and may be employed with specific configurations suitable to the particular application envisioned.

Table 1 represents actual performance measured on an example embodiment cooling fan array in accordance with the present invention, compared to axial fans in series, as described in “prior art” FIGS. 1 and 2.

TABLE 1 Delta from Example Axial Fans in series Example Embodiment (FIG 1&2) Embodiment Air Flow 295 cfm 295 cfm — Static Pressure 2.9 in. of H₂O 2.9 in. of H₂O — Tip Speed 5700 ft/min 13,000 ft/min +128% Sound Power Est. 75 dBA Est. 90 dBA +15 dBA Physical Volume 27 × 10⁵ mm³ 21 × 10⁵ mm³  −22%

Table 2 represents actual performance of an example embodiment cooling fan array in accordance with the present invention, compared to conventional single width, single inlet centrifugal blowers.

TABLE 2 Single width, single Delta from Example inlet Example Embodiment FC Centrifugal Embodiment Air Flow 295 cfm 295 cfm — Static Pressure 2.9 in. of H₂O 2.9 in. of H₂O — Tip Speed 5700 ft/min 5,000 ft/min  −12% Sound Power Est. 75 dBA Est. 73 dBA −2 dBA Physical Volume 27 × 10⁵ mm³ 42 × 10⁵ mm³ +155%

It is clear from the above data that the arrangements of the present invention are capable of producing similar air performance to conventional arrangements, while substantially reducing tip speed, which is a major indicator of acoustic levels. The present arrangements also have substantially reduced volume in comparison to conventional centrifugal blower arrangements, due primarily to the discovery of desired aerodynamic performance with significantly reduced spacing dimensions “x” between respective facing inlets of axially adjacent centrifugal blowers. The surprising aerodynamic performance permits the construction of a highly compact array of centrifugal blowers to achieve either greater performance than conventional arrangements of similar size, or reduced noise output in comparison of conventional blower arrangements of similar size.

The cooling fan arrays of the present invention, therefore, provide substantially enhanced efficiency and reduced acoustic signatures, without requiring substantially increased volume to the housing.

The invention has been described herein in considerable detail in order to comply with the patent statutes, and to provide those skilled in the art with the information needed to apply the novel principles and to construct and use embodiments of the invention as required. However, it is to be understood that the invention can be carried out by specifically different methods/devices and that various modifications can be accomplished without departing from the scope of the invention itself. 

What is claimed is:
 1. A cooling fan array for motivating cooling fluid through an interior chamber of an electronics chassis generally along a flow direction, said array comprising: a frame having a cooling fluid entrance and a cooling fluid exit in fluid communication with the interior chamber, with at least one of said frame entrance and exit directing the cooling fluid flow along a direction parallel with said flow direction, and a plurality of modules each comprising a centrifugal blower with an impeller driven by a motor and defining an axis of rotation, said blower having an inlet arranged to intake the cooling fluid along a respective intake direction transverse to said flow direction, wherein said blowers are arranged in said frame in one or more sets, with each set including at least two blowers oriented with respective inlets in facing relationship with one another and with respective axes of rotation being axially aligned with one another, said facing inlets being axially spaced apart by a spacing dimension that is less than 75% of a diameter dimension of said impeller within said set, such that said blowers operate in parallel to motivate the cooling fluid through said cooling fluid entrance, wherein said modules define a height dimension between said cooling fluid entrance and said cooling fluid exit of 40-50 mm.
 2. A cooling fan array as in claim 1 wherein each of said blowers include a single scroll blower frame defining said dual opposed inlets and a blower outlet, and a forward-curved impeller.
 3. A cooling fan array as in claim 2, including a separation plate defining an outlet plenum of said frame wherein said outlet plenum is fluidly connected to said cooling fluid inlet only through said blowers.
 4. A cooling fan array as in claim 3 wherein said outlet plenum is fluidly connected to said cooling fluid exit.
 5. A cooling fan array as in claim 4, including a divergent outlet duct in said outlet plenum defining a separate outlet flow path from said blower outlet to said cooling fluid exit.
 6. A cooling fan array as in claim 5 wherein said divergent outlet duct has an increasing cross-sectional area from a first location proximal to said blower outlet to a second location distal to said bower outlet.
 7. A cooling fan array as in claim 1, said spacing dimension is 50-75% of a largest one of said diameter dimension of said impeller within said set.
 8. A cooling fan array for motivating air through an interior chamber of an electronic chassis, said array comprising: a first module aligned within an interior chamber of an electronic chassis to motivate air between a cooling air inlet and a cooling air exit of said electronic chassis, said first module including at least one centrifugal blower unit having two opposing air inlets; a second module aligned within the interior chamber of the electronic chassis to motivate air between the cooling air inlet and the cooling air exit of said electronic chassis, said second module including at least one centrifugal blower unit having two opposing air inlets; wherein one of said air inlets of said centrifugal blower unit of said first module operates within an air flow field of one of said air inlets of said centrifugal blower unit of said second module; each said centrifugal blower units having an axis of rotation aligned transverse to the direction of flow of air between the cooling air inlet and the cooling air exit; and wherein the axis of rotation of the centrifugal blower of said first module is aligned parallel with the axis of rotation of the cooling air inlet of said second module.
 9. The cooling fan array according to claim 8, wherein a distance between said air inlet of said centrifugal blower of said first module that operates within the air flow field of one of said air inlets of said centrifugal blower of said second module is less than 75% of a diameter dimension of a largest diameter impeller of said centrifugal blowers of said first and second modules.
 10. The cooling fan array according to claim 9, wherein the largest diameter impeller of said centrifugal blowers has a diameter less than 50 mm.
 11. The cooling fan array according to claim 8 wherein each of said blowers include a single scroll blower frame that defines said opposing air inlets and a single blower outlet.
 12. The cooling fan array according to claim 8, further including a separation plate defining an outlet plenum that isolates said air inlets of each said blower from the cooling air inlet.
 13. The cooling fan array according to claim 8, wherein air enters the cooling air inlet in a direction transverse to the direction of flow of air between the cooling air inlet and the cooling air exit.
 14. A cooling fan array for motivating air through an interior chamber of an electronic chassis, said array comprising: a first module aligned within an interior chamber of an electronic chassis to motivate air between a cooling air inlet and a cooling air exit of said electronic chassis, said first module including a centrifugal blower unit having two opposing air inlets; a second module aligned within the interior chamber of the electronic chassis to motivate air between the cooling air inlet and the cooling air exit of said electronic chassis, said second module including a centrifugal blower unit having two opposing air inlets; a separation plate defining an outlet plenum that isolates said air inlets of each said centrifugal blower unit from the cooling air inlet; wherein one of said air inlets of said centrifugal blower unit of said first module operates within an air flow field of one of said air inlets of said centrifugal blower unit of said second module; each said centrifugal blower unit having an axis of rotation aligned transverse to the direction of flow of air between the cooling air inlet and the cooling air exit; and wherein the axis of rotation of the centrifugal blower of said first module is aligned parallel with the axis of rotation of the cooling air inlet of said second module.
 15. The cooling fan array according to claim 14, wherein a distance between said air inlet of said centrifugal blower of said first module that operates within the air flow field of one of said air inlets of said centrifugal blower of said second module is less than 75% of a diameter dimension of a largest diameter impeller of said centrifugal blowers of said first and second modules.
 16. The cooling fan array according to claim 15, wherein the largest diameter impeller of said centrifugal blowers has a diameter less than 50 mm.
 17. The cooling fan array according to claim 14, wherein each of said blowers include a single scroll blower frame that defines said opposing air inlets and a blower outlet.
 18. The cooling fan array according to claim 14, wherein air enters the cooling air inlet in a direction transverse to the direction of flow of air between the cooling air inlet and the cooling air exit. 